WO2024029247A1 - Unit - Google Patents

Unit Download PDF

Info

Publication number
WO2024029247A1
WO2024029247A1 PCT/JP2023/024214 JP2023024214W WO2024029247A1 WO 2024029247 A1 WO2024029247 A1 WO 2024029247A1 JP 2023024214 W JP2023024214 W JP 2023024214W WO 2024029247 A1 WO2024029247 A1 WO 2024029247A1
Authority
WO
WIPO (PCT)
Prior art keywords
planetary gear
gear mechanism
brake
engagement element
unit
Prior art date
Application number
PCT/JP2023/024214
Other languages
French (fr)
Japanese (ja)
Inventor
秀和 八木
Original Assignee
ジヤトコ株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ジヤトコ株式会社 filed Critical ジヤトコ株式会社
Publication of WO2024029247A1 publication Critical patent/WO2024029247A1/en

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/12—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes
    • F16H1/16—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with non-parallel axes comprising worm and worm-wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly

Definitions

  • the present invention relates to a unit.
  • Patent Document 1 discloses a vehicle drive device in which a rotating electric machine and a transmission are arranged on a first shaft, and a differential gear device is arranged on a second shaft.
  • the speed change gear mechanism of the transmission includes a first planetary gear mechanism including a first one-way clutch and a second planetary gear mechanism including a second one-way clutch. Both the first one-way clutch and the second one-way clutch have a one-way restriction state that restricts rotation in one direction, a two-way restriction state that restricts rotation in both directions, and a release state that allows rotation in both directions. It is a selectable one-way clutch configured to be switchable.
  • the present invention was made in view of these problems, and an object of the present invention is to improve the layout of the unit.
  • a unit includes a first planetary gear mechanism, a second planetary gear mechanism, a first engagement element connected to the first planetary gear mechanism, and a first planetary gear mechanism connected to the second planetary gear mechanism. It has a second engagement element and an actuator that drives at least one of the first engagement element and the second engagement element.
  • the first engagement element has a portion that overlaps with the first planetary gear mechanism.
  • the second engagement element has a portion that overlaps with the second planetary gear mechanism.
  • the first planetary gear mechanism has a portion that overlaps with the second planetary gear mechanism.
  • the actuator has a portion sandwiched between the first engagement element and the second engagement element.
  • the axial dimension can be reduced by radially overlapping each engaging element with each corresponding planetary gear mechanism, thereby improving the layout of the unit. Further, in this case, a certain amount of clearance is required between the two engaging elements so that they do not interfere with each other, so by effectively utilizing that space, the layout of the unit can be further improved.
  • FIG. 1 is a schematic configuration diagram of a unit according to this embodiment.
  • FIG. 2 is a skeleton diagram of the unit.
  • FIG. 3 is a diagram showing a fastening table for the transmission mechanism.
  • FIG. 4A is a first diagram illustrating the switching mechanism.
  • FIG. 4B is a second diagram illustrating the switching mechanism.
  • FIG. 4C is a third diagram illustrating the switching mechanism.
  • FIG. 1 is a schematic configuration diagram of a unit 100 according to this embodiment.
  • FIG. 2 is a skeleton diagram of the unit 100.
  • the unit can also be referred to as, for example, a motor unit (a unit that has at least a motor) or a power transmission device (a device that has at least a power transmission mechanism).
  • the motor is a rotating electric machine having an electric motor function and/or a generator function (at least one of the electric motor function and the generator function).
  • the power transmission mechanism is, for example, a gear mechanism and/or a differential gear mechanism.
  • a device (unit) having a motor and a power transmission mechanism is included in the concepts of both a motor unit and a power transmission device.
  • the unit 100 includes a housing 10 and a transmission mechanism 20.
  • the unit 100 is mounted on a vehicle, and the vehicle is an electric vehicle. Power from the MG 40 is input to the unit 100.
  • MG40 is a rotating electrical machine that functions as a motor generator, and unit 100 can also be understood as a configuration that further includes MG40.
  • the housing 10 houses the transmission mechanism 20.
  • the transmission mechanism 20 includes a case 21, a rotating shaft 22, a first planetary gear mechanism PGM1, a second planetary gear mechanism PGM2, a first brake B1, a second brake B2, and a clutch CL.
  • the case 21 has a cylindrical shape and is fixed to the inner periphery of the housing 10. Inside the case 21, a first planetary gear mechanism PGM1 is provided via a first brake B1, and a second planetary gear mechanism PGM2 is provided via a second brake B2.
  • the rotating shaft 22 is connected to the MG 40 and rotates by power from the MG 40.
  • the extending direction of the rotating shaft 22 corresponds to the axial direction of the unit 100, and the axial direction means the axial direction of the rotating shaft of a component (for example, a motor, a gear mechanism, or a differential gear mechanism) that constitutes the unit.
  • a component for example, a motor, a gear mechanism, or a differential gear mechanism
  • the first planetary gear mechanism PGM1 includes a first sun gear S1, a first carrier C1, a first ring gear R1, and a first pinion gear P1.
  • the first sun gear S1 is coaxially fixed to the rotating shaft 22.
  • the first carrier C1 rotatably supports the first pinion gear P1.
  • the first pinion gear P1 meshes with both the first sun gear S1 and the first ring gear R1.
  • the second planetary gear mechanism PGM2 is arranged in line with the first planetary gear mechanism PGM1 in the axial direction. Therefore, the first planetary gear mechanism PGM1 has a portion that overlaps with the second planetary gear mechanism PGM2 when viewed in the axial direction.
  • Overlapping in a predetermined direction including a radial view and an axial view means overlapping in a predetermined direction, and means that a plurality of elements are lined up in a predetermined direction. From this, if a drawing shows multiple elements lined up in a predetermined direction, it can be assumed that there is a sentence in the specification explaining that multiple elements overlap when viewed in a predetermined direction. .
  • the second planetary gear mechanism PGM2 is provided on the side away from the MG40 with respect to the first planetary gear mechanism PGM1.
  • the second carrier C2 is connected to the first ring gear R1 by being formed integrally with the first ring gear R1.
  • the second carrier C2 constitutes an output element of the second planetary gear mechanism PGM2.
  • the first carrier C1 constitutes the output element of the first planetary gear mechanism PGM1, and also constitutes the output element of the entire first planetary gear mechanism PGM1 and second planetary gear mechanism PGM2, thereby controlling the entire transmission mechanism 20. Configure output elements.
  • the first brake B1 is provided on the outer periphery of the first ring gear R1, and is connected to the first planetary gear mechanism PGM1. Further, the second brake B2 is provided on the outer periphery of the second ring gear R2, and is connected to the second planetary gear mechanism PGM2. Therefore, the first brake B1 has a portion that overlaps with the first planetary gear mechanism PGM1 when viewed in the radial direction, and the second brake B2 has a portion that overlaps with the second planetary gear mechanism PGM2 when viewed in the radial direction.
  • the first brake B1 and the second brake B2 are both meshing engagement elements and have a meshing and fastening structure.
  • the first ring gear R1 is fixed to the case 21 together with the second carrier C2.
  • the first ring gear R1 is fixed to the housing 10 together with the second carrier C2.
  • the second ring gear R2 is fixed to the case 21.
  • the second ring gear R2 is fixed to the housing 10.
  • the first brake B1 corresponds to a first engagement element
  • the second brake B2 corresponds to a second engagement element.
  • Clutch CL is arranged axially side by side with second planetary gear mechanism PGM2 from the side away from MG40.
  • the clutch CL is provided for the rotating shaft 22 and the second carrier C2, and connects and disconnects them.
  • Clutch CL is a friction engagement element and is a multi-disc clutch.
  • the clutch CL is, for example, an electric clutch, and includes a hub 23, a drum 24, a plurality of drive plates 25, a plurality of driven plates 26, and a piston 27.
  • the hub 23 is coaxially fixed to the rotating shaft 22.
  • the hub 23 has an inner cylindrical part 23a, an outer cylindrical part 23b, and a bottom wall part 23c connecting these parts, and is coaxially fixed to the rotating shaft 22 by the inner cylindrical part 23a.
  • the drum 24 has a cylindrical portion 24a and a bottom wall portion 24b, and is provided coaxially with the rotating shaft 22.
  • the drum 24 opens in the direction away from the MG 40.
  • a hub 23 is housed in the drum 24, and the outer periphery of the outer cylindrical portion 23b of the hub 23 faces the inner periphery of the cylindrical portion 24a of the drum 24.
  • the drum 24 is fixedly connected to the second carrier C2 by a ring plate-shaped bottom wall portion 24b.
  • a plurality of drive plates 25 are provided on the hub 23.
  • the plurality of drive plates 25 have a ring shape and are provided on the outer periphery of the outer cylindrical portion 23b so as to be slidable in the axial direction.
  • a plurality of driven plates 26 are provided on the drum 24.
  • the plurality of driven plates 26 have a ring shape and are provided on the inner periphery of the cylindrical portion 24a so as to be slidable in the axial direction.
  • the plurality of drive plates 25 and the plurality of driven plates 26 are arranged alternately one by one in the axial direction.
  • the piston 27 is provided within the drum 24.
  • the piston 27 is slidably provided on the inner periphery of the open end of the drum 24.
  • the piston 27 is, for example, an electric piston driven by an electric actuator of the clutch CL, and by moving in the engagement direction (rightward direction in FIG. 1) and disengagement direction (leftward direction in FIG. 1) of the clutch CL, it The drive plate 25 and the plurality of driven plates 26 are engaged and disengaged from each other.
  • the clutch CL When the plurality of drive plates 25 and the plurality of driven plates 26 are pushed in the engagement direction by the piston 27 and engaged, the clutch CL enters the engaged state. As a result, the rotating shaft 22 and the second carrier C2 are connected via the clutch CL. Furthermore, when the piston 27 moves in the disengagement direction from this state and the plurality of drive plates 25 and the plurality of driven plates 26 are no longer engaged, the clutch CL enters the disengaged state. As a result, the connection between the rotating shaft 22 and the second carrier C2 via the clutch CL is cut off.
  • the gear stages are formed as follows depending on the engagement and release states of the clutch CL, the first brake B1, and the second brake B2.
  • FIG. 3 is a diagram showing a fastening table for the transmission mechanism 20.
  • the transmission mechanism 20 is configured as a three-stage transmission mechanism having three speeds: 1st, 2nd, and 3rd, that is, 1st, 2nd, and 3rd speeds.
  • the first speed is achieved by engaging the first brake B1 and releasing the second brake B2 and clutch CL.
  • Second speed is achieved by engaging the second brake B2 and releasing the first brake B1 and clutch CL.
  • Third speed is achieved by engaging clutch CL and releasing first brake B1 and second brake B2.
  • the unit 100 further includes a drive device 30.
  • the drive device 30 is a drive device for the first brake B1 and the second brake B2, and includes an actuator 31 and a worm wheel 32.
  • the actuator 31 is schematically shown with a two-dot broken line.
  • the actuator 31 is an electric motor and has a worm gear 311.
  • the worm gear 311 constitutes a rotating shaft of the actuator 31 and meshes with the worm wheel 32.
  • the worm shaft of the worm gear 311 and the center axis of the worm wheel 32 are orthogonal to each other, and the worm wheel 32 is provided so as to be rotatably driven around the axis of the unit 100 by power from the actuator 31. Therefore, the longitudinal direction of the worm gear 311, which is the worm axis direction, intersects with the axial direction of the unit 100.
  • the worm gear 311 is provided between the first brake B1 and the second brake B2 in the axial direction of the unit 100. Therefore, the actuator 31 has a portion sandwiched between the first brake B1 and the second brake B2. In the actuator 31, the worm gear 311 has such a portion.
  • the worm wheel 32 is provided between the first planetary gear mechanism PGM1 and the second planetary gear mechanism PGM2 in the axial direction of the unit 100.
  • the first brake B1 has a first switching mechanism SWM1
  • the second brake B2 has a second switching mechanism SWM2.
  • the first switching mechanism SWM1 switches the engagement state of the first brake B1
  • the second switching mechanism SWM2 switches the engagement state of the second brake B2.
  • FIGS. 4A to 4C are explanatory diagrams of the switching mechanism SWM.
  • FIG. 4A shows the first switching mechanism SWM1 in a bidirectional restricted state.
  • FIG. 4B shows the first switching mechanism SWM1 in a one-way restricted state.
  • FIG. 4C shows the first switching mechanism SWM1 in a released state.
  • the first switching mechanism SWM1 will be described as an example of the switching mechanism SWM in FIGS. 4A to 4C, the same applies to the second switching mechanism SWM2.
  • the first switching mechanism SWM1 includes a first stationary member CB1, a first rotating member RB1, a first claw CW1, and a first switching part SW1.
  • the first fixed member CB1 has a ring shape and is fixed to the inner periphery of the case 21.
  • the first pawl CW1 is an engaging portion and is installed on the first fixed side member CB1 at a portion that projects inward in the radial direction. A plurality of the portions are provided along the circumferential direction, and two first claws CW1 are provided as one set of claws for each portion. In one set of claws, each of the first claws CW1 is provided in opposite directions to correspond to the bidirectional rotational directions.
  • the first claw CW1 has a structure in which a radially inner tip portion rotates around a radially outer base end portion.
  • the first claw CW1 is switched between a lock position for locking the rotation of the first ring gear R1 and a free position for freeing the rotation of the first ring gear R1, and is biased to the lock position by a spring serving as a biasing member. Therefore, in the state shown in FIG. 4A, each of the first claws CW1 is pushed to the lock position by the spring.
  • the first rotating member RB1 is fixed to the outer periphery of the first ring gear R1.
  • the first rotation-side member RB1 has a ring-like shape, and has an engaging portion on its outer periphery that is constituted by a plurality of convex portions evenly provided in the circumferential direction.
  • the first pawl CW1 engages with the engaging portion, and forms an interlocking fastening structure together with the engaging portion.
  • the first pawl CW1 prevents the first ring gear R1 from rotating in one rotational direction, and allows the first ring gear R1 to rotate in the other rotational direction.
  • the first pawl CW1 on the left side of one set of left and right pawls in the figure prevents the first ring gear R1 from rotating when the tip rotates in the right direction in the figure without escaping to the outside in the radial direction.
  • the tip portion escapes radially outward, allowing rotation of the first ring gear R1.
  • the first pawl CW1 on the right side prevents the first ring gear R1 from rotating in the left direction, and allows the first ring gear R1 to rotate in the right direction.
  • the bidirectional restriction state shown in FIG. 4A rotation of the first ring gear R1 in both left and right directions is restricted. Therefore, the first brake B1 is engaged when the first ring gear R1 rotates in both directions.
  • the first switching part SW1 has a first switching plate PL1, and switches the position of the first claw CW1.
  • the first switching plate PL1 of the first switching unit SW1 is indicated by a two-dot broken line.
  • the first switching plate PL1 has a ring shape and is movable in the circumferential direction.
  • the first switching plate PL1 has a position corresponding to the bidirectional restriction state shown in FIG. 4A, a position corresponding to the one-way restriction state shown in FIG. 4B, and a position corresponding to the release state shown in FIG. 4C.
  • the first switching plate PL1 is provided on the worm wheel 32 and rotates together with the worm wheel 32. Therefore, the first switching plate PL1 is driven in the circumferential direction by the actuator 31, thereby switching the position of the first switching plate PL1.
  • the first switching plate PL1 when the first switching plate PL1 is rotationally driven to a fixed position on the right side from the state shown in FIG. 4A, the position of the first switching plate PL1 is switched to a position corresponding to the one-way restriction state shown in FIG. 4B.
  • the first switching part SW1 switches the position of the left first pawl CW1 to the free position by pushing the tip of the left first pawl CW1 radially outward against the biasing force of the spring. .
  • the left first pawl CW1 is disengaged from the engagement portion of the first rotating member RB1, and the first ring gear R1 is free to rotate rightward.
  • the right first pawl CW1 remains engaged with the engaging portion, so the rotation of the first ring gear R1 in the leftward direction is locked. Therefore, in this case, the first brake B1 is released against the rotation of the first ring gear R1 in the rightward direction, and is in the engaged state against the rotation of the first ring gear R1 in the leftward direction.
  • the first switching plate PL1 When the first switching plate PL1 is rotationally driven to a fixed position on the left side from the state shown in FIG. 4A, the position of the first switching plate PL1 is switched to a position corresponding to the released state shown in FIG. 4C. At this time, the first switching part SW1 pushes the tips of both the left and right first claws CW1 radially outward against the biasing force of the spring, thereby changing the positions of both the left and right first claws CW1 to the free position. Switch to As a result, the first ring gear R1 can freely rotate in both left and right directions.
  • the actuator 31 drives the first brake B1 by driving the first switching plate PL1.
  • the actuator 31 can also drive the second brake B2 in the same manner as the first brake B1.
  • the unit 100 includes a first planetary gear mechanism PGM1, a second planetary gear mechanism PGM2, a first brake B1 connected to the first planetary gear mechanism PGM1, and a second brake B1 connected to the second planetary gear mechanism PGM2. It has a brake B2 and an actuator 31 that drives the first brake B1 and the second brake B2.
  • the first brake B1 has a portion that overlaps with the first planetary gear mechanism PGM1.
  • the second brake B2 has a portion that overlaps with the second planetary gear mechanism PGM2.
  • the first planetary gear mechanism PGM1 has a portion that overlaps with the second planetary gear mechanism PGM2.
  • the actuator 31 has a portion sandwiched between a first brake B1 and a second brake B2.
  • the shaft Directional dimensions can be reduced. Therefore, the layout of the unit 100 is improved. Also, at this time, a certain amount of clearance is required between the first brake B1 and the second brake B2 so that they do not interfere with each other, so by making effective use of that space, the layout of the unit 100 can be further improved. can.
  • the actuator 31 may be configured to drive the first brake B1 or the second brake B2. Even in this case, similar effects can be obtained.
  • the actuator 31 drives both the first brake B1 and the second brake B2. According to such a configuration, the number of parts can be reduced by sharing the actuator 31 between the first brake B1 and the second brake B2, and the layout of the unit 100 can also be improved by reducing the number of parts.
  • the actuator 31 has a worm gear 311.
  • the worm gear 311 has a portion sandwiched between the first brake B1 and the second brake B2, and the longitudinal direction of the worm gear 311 intersects with the axial direction of the unit 100. According to such a configuration, when the worm gear 311 of the actuator 31 is sandwiched between the first brake B1 and the second brake B2, its longitudinal direction intersects with the axial direction, thereby contributing to shortening the unit 100 in the axial direction. can do.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

[Problem] To improve layout properties of a unit. [Solution] The unit includes a first planetary gear mechanism, a second planetary gear mechanism, a first engagement element connected to the first planetary gear mechanism, a second engagement element connected to the second planetary gear mechanism, and an actuator driving at least either the first engagement element or the second engagement element. In a radial-direction view, the first engagement element has a portion that overlaps the first planetary gear mechanism. In a radial-direction view, the second engagement element has a portion that overlaps the second planetary gear mechanism. In an axial-direction view, the first planetary gear mechanism has a portion that overlaps the second planetary gear mechanism. The actuator has a portion that is sandwiched between the first engagement element and the second engagement element.

Description

ユニットunit
　本発明はユニットに関する。 The present invention relates to a unit.
　特許文献１には回転電機及び変速機が第１軸上に配置され、差動歯車装置が第２軸上に配置された車両用駆動装置が開示されている。変速機の変速ギヤ機構は第１ワンウェイクラッチを備える第１遊星歯車機構と、第２ワンウェイクラッチを備える第２遊星歯車機構とを備える。第１ワンウェイクラッチと第２ワンウェイクラッチとはともに、一方向の回転を規制する一方向規制状態と、双方向の回転を規制する双方向規制状態と、双方向の回転を許容する解放状態とに切り替え可能に構成されたセレクタブルワンウェイクラッチとされる。 Patent Document 1 discloses a vehicle drive device in which a rotating electric machine and a transmission are arranged on a first shaft, and a differential gear device is arranged on a second shaft. The speed change gear mechanism of the transmission includes a first planetary gear mechanism including a first one-way clutch and a second planetary gear mechanism including a second one-way clutch. Both the first one-way clutch and the second one-way clutch have a one-way restriction state that restricts rotation in one direction, a two-way restriction state that restricts rotation in both directions, and a release state that allows rotation in both directions. It is a selectable one-way clutch configured to be switchable.
特開２０２０－１７５７０７号公報Japanese Patent Application Publication No. 2020-175707
　複数の遊星歯車機構を用いてユニットの動力伝達機構を構成する場合、ユニットにおいて効率的なレイアウトを実現することにより小型化を図り、ユニットのレイアウト性を高めることが望まれる。 When configuring the power transmission mechanism of a unit using a plurality of planetary gear mechanisms, it is desirable to realize an efficient layout in the unit to achieve miniaturization and improve the layout of the unit.
　本発明はこのような課題に鑑みてなされたもので、ユニットのレイアウト性を向上させることを目的とする。 The present invention was made in view of these problems, and an object of the present invention is to improve the layout of the unit.
　本発明のある態様のユニットは、第１遊星歯車機構と、第２遊星歯車機構と、前記第１遊星歯車機構に接続された第１係合要素と、前記第２遊星歯車機構に接続された第２係合要素と、前記第１係合要素及び前記第２係合要素の少なくとも一方を駆動するアクチュエータとを有する。径方向視において、前記第１係合要素は前記第１遊星歯車機構とオーバーラップする部分を有する。径方向視において、前記第２係合要素は前記第２遊星歯車機構とオーバーラップする部分を有する。軸方向視において、前記第１遊星歯車機構は前記第２遊星歯車機構とオーバーラップする部分を有する。前記アクチュエータは前記第１係合要素及び前記第２係合要素の間に挟まれた部分を有する。 A unit according to an aspect of the present invention includes a first planetary gear mechanism, a second planetary gear mechanism, a first engagement element connected to the first planetary gear mechanism, and a first planetary gear mechanism connected to the second planetary gear mechanism. It has a second engagement element and an actuator that drives at least one of the first engagement element and the second engagement element. In a radial view, the first engagement element has a portion that overlaps with the first planetary gear mechanism. In a radial view, the second engagement element has a portion that overlaps with the second planetary gear mechanism. When viewed in the axial direction, the first planetary gear mechanism has a portion that overlaps with the second planetary gear mechanism. The actuator has a portion sandwiched between the first engagement element and the second engagement element.
　この態様によれば、係合要素それぞれを対応する遊星歯車機構それぞれと径方向においてオーバーラップさせることで軸方向の寸法を縮小できるので、ユニットのレイアウト性が向上する。またこのときには２つの係合要素の間に両者が干渉しないようにそれなりのクリアランスが必要になるので、そのスペースを有効利用することにより、ユニットのレイアウト性をさらに向上させることができる。 According to this aspect, the axial dimension can be reduced by radially overlapping each engaging element with each corresponding planetary gear mechanism, thereby improving the layout of the unit. Further, in this case, a certain amount of clearance is required between the two engaging elements so that they do not interfere with each other, so by effectively utilizing that space, the layout of the unit can be further improved.
図１は、本実施形態にかかるユニットの概略構成図である。FIG. 1 is a schematic configuration diagram of a unit according to this embodiment. 図２は、ユニットのスケルトン図である。FIG. 2 is a skeleton diagram of the unit. 図３は、変速機構の締結表を示す図である。FIG. 3 is a diagram showing a fastening table for the transmission mechanism. 図４Ａは、切替機構の説明図の第１図である。FIG. 4A is a first diagram illustrating the switching mechanism. 図４Ｂは、切替機構の説明図の第２図である。FIG. 4B is a second diagram illustrating the switching mechanism. 図４Ｃは、切替機構の説明図の第３図である。FIG. 4C is a third diagram illustrating the switching mechanism.
　以下、添付図面を参照しながら本発明の実施形態について説明する。 Embodiments of the present invention will be described below with reference to the accompanying drawings.
　図１は本実施形態にかかるユニット１００の概略構成図である。図２はユニット１００のスケルトン図である。 FIG. 1 is a schematic configuration diagram of a unit 100 according to this embodiment. FIG. 2 is a skeleton diagram of the unit 100.
　ユニットの語に関し、ユニットは例えばモータユニット（少なくともモータを有するユニット）や、動力伝達装置（少なくとも動力伝達機構を有する装置）とも称することができる。モータは電動機機能及び／又は発電機機能（電動機機能及び発電機機能のうち少なくともいずれか）を有する回転電機である。動力伝達機構は例えば歯車機構及び／又は差動歯車機構である。モータ及び動力伝達機構を有する装置（ユニット）はモータユニット及び動力伝達装置の双方の概念に含まれる。 Regarding the word unit, the unit can also be referred to as, for example, a motor unit (a unit that has at least a motor) or a power transmission device (a device that has at least a power transmission mechanism). The motor is a rotating electric machine having an electric motor function and/or a generator function (at least one of the electric motor function and the generator function). The power transmission mechanism is, for example, a gear mechanism and/or a differential gear mechanism. A device (unit) having a motor and a power transmission mechanism is included in the concepts of both a motor unit and a power transmission device.
　図１に示すように、ユニット１００はハウジング１０と変速機構２０とを備える。ユニット１００は車両に搭載され、当該車両は電動車両とされる。ユニット１００にはＭＧ４０からの動力が入力される。ＭＧ４０はモータジェネレータとして機能する回転電機であり、ユニット１００はＭＧ４０をさらに含む構成として把握することもできる。 As shown in FIG. 1, the unit 100 includes a housing 10 and a transmission mechanism 20. The unit 100 is mounted on a vehicle, and the vehicle is an electric vehicle. Power from the MG 40 is input to the unit 100. MG40 is a rotating electrical machine that functions as a motor generator, and unit 100 can also be understood as a configuration that further includes MG40.
　ハウジング１０は変速機構２０を収容する。変速機構２０はケース２１と回転軸２２と第１遊星歯車機構ＰＧＭ１と第２遊星歯車機構ＰＧＭ２と第１ブレーキＢ１と第２ブレーキＢ２とクラッチＣＬとを備える。ケース２１は筒状の形状を有し、ハウジング１０の内周に固定される。ケース２１内には第１ブレーキＢ１を介して第１遊星歯車機構ＰＧＭ１が設けられるとともに、第２ブレーキＢ２を介して第２遊星歯車機構ＰＧＭ２が設けられる。回転軸２２はＭＧ４０に接続され、ＭＧ４０からの動力により回転する。回転軸２２の延伸方向はユニット１００の軸方向に相当し、当該軸方向はユニットを構成する部品（例えばモータや歯車機構や差動歯車機構）の回転軸の軸方向を意味する。 The housing 10 houses the transmission mechanism 20. The transmission mechanism 20 includes a case 21, a rotating shaft 22, a first planetary gear mechanism PGM1, a second planetary gear mechanism PGM2, a first brake B1, a second brake B2, and a clutch CL. The case 21 has a cylindrical shape and is fixed to the inner periphery of the housing 10. Inside the case 21, a first planetary gear mechanism PGM1 is provided via a first brake B1, and a second planetary gear mechanism PGM2 is provided via a second brake B2. The rotating shaft 22 is connected to the MG 40 and rotates by power from the MG 40. The extending direction of the rotating shaft 22 corresponds to the axial direction of the unit 100, and the axial direction means the axial direction of the rotating shaft of a component (for example, a motor, a gear mechanism, or a differential gear mechanism) that constitutes the unit.
　第１遊星歯車機構ＰＧＭ１は第１サンギアＳ１、第１キャリアＣ１、第１リングギアＲ１及び第１ピニオンギアＰ１を備える。第１サンギアＳ１は回転軸２２に同軸状に固定される。第１キャリアＣ１は第１ピニオンギアＰ１を回転自在に支持する。第１ピニオンギアＰ１は第１サンギアＳ１及び第１リングギアＲ１の双方と噛み合う。これらのことは、第２サンギアＳ２、第２キャリアＣ２、第２リングギアＲ２及び第２ピニオンギアＰ２を備える第２遊星歯車機構ＰＧＭ２についても同様である。 The first planetary gear mechanism PGM1 includes a first sun gear S1, a first carrier C1, a first ring gear R1, and a first pinion gear P1. The first sun gear S1 is coaxially fixed to the rotating shaft 22. The first carrier C1 rotatably supports the first pinion gear P1. The first pinion gear P1 meshes with both the first sun gear S1 and the first ring gear R1. The same applies to the second planetary gear mechanism PGM2 including the second sun gear S2, second carrier C2, second ring gear R2, and second pinion gear P2.
　第２遊星歯車機構ＰＧＭ２は第１遊星歯車機構ＰＧＭ１と軸方向に並んで配置される。従って、第１遊星歯車機構ＰＧＭ１は軸方向視で第２遊星歯車機構ＰＧＭ２とオーバーラップする部分を有する。径方向視や軸方向視を含む所定方向視でオーバーラップするとは、所定方向にオーバーラップするということであり、所定方向に複数の要素が並んでいることを意味する。このことから、図面において複数の要素が所定方向に並んでいることが図示されている場合は、明細書において所定方向視で複数の要素がオーバーラップすることを説明した文章があるとみなしてよい。 The second planetary gear mechanism PGM2 is arranged in line with the first planetary gear mechanism PGM1 in the axial direction. Therefore, the first planetary gear mechanism PGM1 has a portion that overlaps with the second planetary gear mechanism PGM2 when viewed in the axial direction. Overlapping in a predetermined direction including a radial view and an axial view means overlapping in a predetermined direction, and means that a plurality of elements are lined up in a predetermined direction. From this, if a drawing shows multiple elements lined up in a predetermined direction, it can be assumed that there is a sentence in the specification explaining that multiple elements overlap when viewed in a predetermined direction. .
　第２遊星歯車機構ＰＧＭ２は第１遊星歯車機構ＰＧＭ１に対しＭＧ４０から離れる側に設けられる。第２キャリアＣ２は第１リングギアＲ１と一体形成されることで、第１リングギアＲ１と接続する。第２キャリアＣ２は第２遊星歯車機構ＰＧＭ２の出力要素を構成する。これに対し、第１キャリアＣ１は第１遊星歯車機構ＰＧＭ１の出力要素を構成するとともに、第１遊星歯車機構ＰＧＭ１及び第２遊星歯車機構ＰＧＭ２全体の出力要素を構成することで変速機構２０全体の出力要素を構成する。 The second planetary gear mechanism PGM2 is provided on the side away from the MG40 with respect to the first planetary gear mechanism PGM1. The second carrier C2 is connected to the first ring gear R1 by being formed integrally with the first ring gear R1. The second carrier C2 constitutes an output element of the second planetary gear mechanism PGM2. On the other hand, the first carrier C1 constitutes the output element of the first planetary gear mechanism PGM1, and also constitutes the output element of the entire first planetary gear mechanism PGM1 and second planetary gear mechanism PGM2, thereby controlling the entire transmission mechanism 20. Configure output elements.
　第１ブレーキＢ１は第１リングギアＲ１の外周に設けられ、第１遊星歯車機構ＰＧＭ１に接続される。また、第２ブレーキＢ２は第２リングギアＲ２の外周に設けられ、第２遊星歯車機構ＰＧＭ２に接続される。従って、第１ブレーキＢ１は径方向視で第１遊星歯車機構ＰＧＭ１とオーバーラップする部分を有し、第２ブレーキＢ２は径方向視で第２遊星歯車機構ＰＧＭ２とオーバーラップする部分を有する。 The first brake B1 is provided on the outer periphery of the first ring gear R1, and is connected to the first planetary gear mechanism PGM1. Further, the second brake B2 is provided on the outer periphery of the second ring gear R2, and is connected to the second planetary gear mechanism PGM2. Therefore, the first brake B1 has a portion that overlaps with the first planetary gear mechanism PGM1 when viewed in the radial direction, and the second brake B2 has a portion that overlaps with the second planetary gear mechanism PGM2 when viewed in the radial direction.
　第１ブレーキＢ１及び第２ブレーキＢ２はともに噛合係合要素であり、噛み合い締結構造を有する。第１ブレーキＢ１が締結すると、第１リングギアＲ１が第２キャリアＣ２とともにケース２１に固定される。結果、第１リングギアＲ１が第２キャリアＣ２とともにハウジング１０に固定される。第２ブレーキＢ２が締結すると、第２リングギアＲ２がケース２１に固定される。結果、第２リングギアＲ２がハウジング１０に固定される。第１ブレーキＢ１は第１係合要素に相当し、第２ブレーキＢ２は第２係合要素に相当する。 The first brake B1 and the second brake B2 are both meshing engagement elements and have a meshing and fastening structure. When the first brake B1 is engaged, the first ring gear R1 is fixed to the case 21 together with the second carrier C2. As a result, the first ring gear R1 is fixed to the housing 10 together with the second carrier C2. When the second brake B2 is engaged, the second ring gear R2 is fixed to the case 21. As a result, the second ring gear R2 is fixed to the housing 10. The first brake B1 corresponds to a first engagement element, and the second brake B2 corresponds to a second engagement element.
　クラッチＣＬはＭＧ４０から離れる側から第２遊星歯車機構ＰＧＭ２と軸方向に並べて配置される。クラッチＣＬは回転軸２２と第２キャリアＣ２とに対して設けられ、これらの接続及び遮断を行う。クラッチＣＬは摩擦係合要素であり、多板クラッチとされる。クラッチＣＬは例えば電動クラッチであり、ハブ２３とドラム２４と複数のドライブプレート２５と複数のドリブンプレート２６とピストン２７とを備える。 Clutch CL is arranged axially side by side with second planetary gear mechanism PGM2 from the side away from MG40. The clutch CL is provided for the rotating shaft 22 and the second carrier C2, and connects and disconnects them. Clutch CL is a friction engagement element and is a multi-disc clutch. The clutch CL is, for example, an electric clutch, and includes a hub 23, a drum 24, a plurality of drive plates 25, a plurality of driven plates 26, and a piston 27.
　ハブ２３は回転軸２２に同軸状に固定される。ハブ２３は内側筒状部２３ａと外側筒状部２３ｂとこれらを繋ぐ底壁部２３ｃとを有し、内側筒状部２３ａで回転軸２２に同軸状に固定される。ドラム２４は筒状部２４ａと底壁部２４ｂとを有し、回転軸２２に対して同軸状に設けられる。ドラム２４はＭＧ４０から離れる方向に向かって開口する。ドラム２４内にはハブ２３が収容され、ハブ２３の外側筒状部２３ｂの外周はドラム２４の筒状部２４ａの内周と対向する。ドラム２４はリングプレート状の底壁部２４ｂで第２キャリアＣ２と固定接続される。 The hub 23 is coaxially fixed to the rotating shaft 22. The hub 23 has an inner cylindrical part 23a, an outer cylindrical part 23b, and a bottom wall part 23c connecting these parts, and is coaxially fixed to the rotating shaft 22 by the inner cylindrical part 23a. The drum 24 has a cylindrical portion 24a and a bottom wall portion 24b, and is provided coaxially with the rotating shaft 22. The drum 24 opens in the direction away from the MG 40. A hub 23 is housed in the drum 24, and the outer periphery of the outer cylindrical portion 23b of the hub 23 faces the inner periphery of the cylindrical portion 24a of the drum 24. The drum 24 is fixedly connected to the second carrier C2 by a ring plate-shaped bottom wall portion 24b.
　複数のドライブプレート２５はハブ２３に設けられる。複数のドライブプレート２５はリング状の形状を有し、外側筒状部２３ｂの外周に軸方向に摺動可能に設けられる。複数のドリブンプレート２６はドラム２４に設けられる。複数のドリブンプレート２６はリング状の形状を有し、筒状部２４ａの内周に軸方向に摺動可能に設けられる。複数のドライブプレート２５と複数のドリブンプレート２６とは軸方向に一枚ずつ交互に並べて設けられる。 A plurality of drive plates 25 are provided on the hub 23. The plurality of drive plates 25 have a ring shape and are provided on the outer periphery of the outer cylindrical portion 23b so as to be slidable in the axial direction. A plurality of driven plates 26 are provided on the drum 24. The plurality of driven plates 26 have a ring shape and are provided on the inner periphery of the cylindrical portion 24a so as to be slidable in the axial direction. The plurality of drive plates 25 and the plurality of driven plates 26 are arranged alternately one by one in the axial direction.
　ピストン２７はドラム２４内に設けられる。ピストン２７はドラム２４の開口端部内周に摺動可能に設けられる。ピストン２７は例えばクラッチＣＬの電動アクチュエータにより駆動される電動ピストンであり、クラッチＣＬの係合方向（図１の右方向）及び係合解除方向（図１の左方向）に移動することで、複数のドライブプレート２５と複数のドリブンプレート２６との係合及び係合解除を行う。 The piston 27 is provided within the drum 24. The piston 27 is slidably provided on the inner periphery of the open end of the drum 24. The piston 27 is, for example, an electric piston driven by an electric actuator of the clutch CL, and by moving in the engagement direction (rightward direction in FIG. 1) and disengagement direction (leftward direction in FIG. 1) of the clutch CL, it The drive plate 25 and the plurality of driven plates 26 are engaged and disengaged from each other.
　複数のドライブプレート２５及び複数のドリブンプレート２６がピストン２７により係合方向に押されて係合すると、クラッチＣＬが係合状態になる。結果、クラッチＣＬを介して回転軸２２と第２キャリアＣ２とが接続される。また、この状態からピストン２７が係合解除方向に移動して複数のドライブプレート２５と複数のドリブンプレート２６とが係合しなくなると、クラッチＣＬが係合解除状態になる。結果、クラッチＣＬを介した回転軸２２と第２キャリアＣ２との接続が遮断される。変速機構２０ではクラッチＣＬ、第１ブレーキＢ１及び第２ブレーキＢ２の締結解放状態に応じて次のように変速段が形成される。 When the plurality of drive plates 25 and the plurality of driven plates 26 are pushed in the engagement direction by the piston 27 and engaged, the clutch CL enters the engaged state. As a result, the rotating shaft 22 and the second carrier C2 are connected via the clutch CL. Furthermore, when the piston 27 moves in the disengagement direction from this state and the plurality of drive plates 25 and the plurality of driven plates 26 are no longer engaged, the clutch CL enters the disengaged state. As a result, the connection between the rotating shaft 22 and the second carrier C2 via the clutch CL is cut off. In the transmission mechanism 20, the gear stages are formed as follows depending on the engagement and release states of the clutch CL, the first brake B1, and the second brake B2.
　図３は変速機構２０の締結表を示す図である。図３に示すように、変速機構２０は１ｓｔ、２ｎｄ及び３ｒｄ、つまり１速、２速及び３速の３つの変速段を有する３段変速機構として構成される。１速は第１ブレーキＢ１を締結し、第２ブレーキＢ２及びクラッチＣＬを解放することにより達成される。２速は第２ブレーキＢ２を締結し、第１ブレーキＢ１及びクラッチＣＬを解放することにより達成される。３速はクラッチＣＬを締結し、第１ブレーキＢ１及び第２ブレーキＢ２を解放することにより達成される。 FIG. 3 is a diagram showing a fastening table for the transmission mechanism 20. As shown in FIG. 3, the transmission mechanism 20 is configured as a three-stage transmission mechanism having three speeds: 1st, 2nd, and 3rd, that is, 1st, 2nd, and 3rd speeds. The first speed is achieved by engaging the first brake B1 and releasing the second brake B2 and clutch CL. Second speed is achieved by engaging the second brake B2 and releasing the first brake B1 and clutch CL. Third speed is achieved by engaging clutch CL and releasing first brake B1 and second brake B2.
　図１に戻り、ユニット１００は駆動装置３０をさらに備える。駆動装置３０は第１ブレーキＢ１及び第２ブレーキＢ２の駆動装置であり、アクチュエータ３１とウォームホイール３２とを有する。図１ではアクチュエータ３１を二点破線で模式的に示す。 Returning to FIG. 1, the unit 100 further includes a drive device 30. The drive device 30 is a drive device for the first brake B1 and the second brake B2, and includes an actuator 31 and a worm wheel 32. In FIG. 1, the actuator 31 is schematically shown with a two-dot broken line.
　アクチュエータ３１は電動モータであり、ウォームギア３１１を有する。ウォームギア３１１はアクチュエータ３１の回転軸を構成し、ウォームホイール３２と噛み合う。ウォームギア３１１のウォーム軸とウォームホイール３２の中心軸とは互いに直交し、ウォームホイール３２はアクチュエータ３１からの動力によりユニット１００の軸心周りに回転駆動可能に設けられる。従って、ウォームギア３１１のウォーム軸方向である長手方向はユニット１００の軸方向と交差する。 The actuator 31 is an electric motor and has a worm gear 311. The worm gear 311 constitutes a rotating shaft of the actuator 31 and meshes with the worm wheel 32. The worm shaft of the worm gear 311 and the center axis of the worm wheel 32 are orthogonal to each other, and the worm wheel 32 is provided so as to be rotatably driven around the axis of the unit 100 by power from the actuator 31. Therefore, the longitudinal direction of the worm gear 311, which is the worm axis direction, intersects with the axial direction of the unit 100.
　ウォームギア３１１はユニット１００の軸方向において第１ブレーキＢ１と第２ブレーキＢ２との間に設けられる。従って、アクチュエータ３１は第１ブレーキＢ１と第２ブレーキＢ２との間に挟まれた部分を有する。アクチュエータ３１ではウォームギア３１１がこのような部分を有する。ウォームホイール３２はユニット１００の軸方向において第１遊星歯車機構ＰＧＭ１と第２遊星歯車機構ＰＧＭ２との間に設けられる。 The worm gear 311 is provided between the first brake B1 and the second brake B2 in the axial direction of the unit 100. Therefore, the actuator 31 has a portion sandwiched between the first brake B1 and the second brake B2. In the actuator 31, the worm gear 311 has such a portion. The worm wheel 32 is provided between the first planetary gear mechanism PGM1 and the second planetary gear mechanism PGM2 in the axial direction of the unit 100.
　第１ブレーキＢ１は第１切替機構ＳＷＭ１を有し、第２ブレーキＢ２は第２切替機構ＳＷＭ２を有する。第１切替機構ＳＷＭ１は第１ブレーキＢ１の係合状態を切り替え、第２切替機構ＳＷＭ２は第２ブレーキＢ２の係合状態を切り替える。 The first brake B1 has a first switching mechanism SWM1, and the second brake B2 has a second switching mechanism SWM2. The first switching mechanism SWM1 switches the engagement state of the first brake B1, and the second switching mechanism SWM2 switches the engagement state of the second brake B2.
　図４Ａから図４Ｃは切替機構ＳＷＭの説明図である。図４Ａでは双方向規制状態で第１切替機構ＳＷＭ１を示す。図４Ｂでは一方向規制状態で第１切替機構ＳＷＭ１を示す。図４Ｃでは解放状態で第１切替機構ＳＷＭ１を示す。図４Ａから図４Ｃでは切替機構ＳＷＭとして第１切替機構ＳＷＭ１を例にして説明するが、第２切替機構ＳＷＭ２についても同様である。 FIGS. 4A to 4C are explanatory diagrams of the switching mechanism SWM. FIG. 4A shows the first switching mechanism SWM1 in a bidirectional restricted state. FIG. 4B shows the first switching mechanism SWM1 in a one-way restricted state. FIG. 4C shows the first switching mechanism SWM1 in a released state. Although the first switching mechanism SWM1 will be described as an example of the switching mechanism SWM in FIGS. 4A to 4C, the same applies to the second switching mechanism SWM2.
　第１切替機構ＳＷＭ１は第１固定側部材ＣＢ１と第１回転側部材ＲＢ１と第１の爪ＣＷ１と第１切替部ＳＷ１とを備える。第１固定側部材ＣＢ１はリング状の形状を有し、ケース２１の内周に固定される。第１の爪ＣＷ１は係合部であり、径方向内側に突出する部分の第１固定側部材ＣＢ１に設置される。当該部分は周方向に沿って複数設けられ、当該部分一つに対して二つの第１の爪ＣＷ１が１セットの爪として設けられる。１セットの爪では第１の爪ＣＷ１それぞれが双方向の回転方向に対応させて互いに逆向きに設けられる。 The first switching mechanism SWM1 includes a first stationary member CB1, a first rotating member RB1, a first claw CW1, and a first switching part SW1. The first fixed member CB1 has a ring shape and is fixed to the inner periphery of the case 21. The first pawl CW1 is an engaging portion and is installed on the first fixed side member CB1 at a portion that projects inward in the radial direction. A plurality of the portions are provided along the circumferential direction, and two first claws CW1 are provided as one set of claws for each portion. In one set of claws, each of the first claws CW1 is provided in opposite directions to correspond to the bidirectional rotational directions.
　第１の爪ＣＷ１は径方向外側の基端部を軸に径方向内側の先端部が回転する構造を有する。第１の爪ＣＷ１は第１リングギアＲ１の回転をロックするロック位置とフリーにするフリー位置とに切り替えられ、付勢部材であるばねによりロック位置に付勢される。従って、図４Ａに示す状態では第１の爪ＣＷ１それぞれはばねによりロック位置に押されている。 The first claw CW1 has a structure in which a radially inner tip portion rotates around a radially outer base end portion. The first claw CW1 is switched between a lock position for locking the rotation of the first ring gear R1 and a free position for freeing the rotation of the first ring gear R1, and is biased to the lock position by a spring serving as a biasing member. Therefore, in the state shown in FIG. 4A, each of the first claws CW1 is pushed to the lock position by the spring.
　第１回転側部材ＲＢ１は第１リングギアＲ１の外周に固定される。第１回転側部材ＲＢ１はリング状の形状を有し、円周方向に均等に設けられた複数の凸部により構成される係合部を外周に有する。当該係合部には第１の爪ＣＷ１が係合し、当該係合部とともに噛み合い締結構造を構成する。第１の爪ＣＷ１は一方の回転方向に対しては第１リングギアＲ１の回転を阻止し、他方の回転方向に対しては第１リングギアＲ１の回転を許容する。 The first rotating member RB1 is fixed to the outer periphery of the first ring gear R1. The first rotation-side member RB1 has a ring-like shape, and has an engaging portion on its outer periphery that is constituted by a plurality of convex portions evenly provided in the circumferential direction. The first pawl CW1 engages with the engaging portion, and forms an interlocking fastening structure together with the engaging portion. The first pawl CW1 prevents the first ring gear R1 from rotating in one rotational direction, and allows the first ring gear R1 to rotate in the other rotational direction.
　例えば、図の左右１セットの爪のうち左側の第１の爪ＣＷ１は図の右方向の回転に対しては先端部が径方向外側に逃げずに第１リングギアＲ１の回転を阻止し、左方向の回転に対しては先端部が径方向外側に逃げることで第１リングギアＲ１の回転を許容する。右側の第１の爪ＣＷ１は左方向の回転に対しては第１リングギアＲ１の回転を阻止し、右方向の回転に対しては第１リングギアＲ１の回転を許容する。結果、図４Ａに示す双方向規制状態では左右双方向への第１リングギアＲ１の回転が規制される。従って、第１リングギアＲ１の双方向の回転に対して、第１ブレーキＢ１が締結状態になる。 For example, the first pawl CW1 on the left side of one set of left and right pawls in the figure prevents the first ring gear R1 from rotating when the tip rotates in the right direction in the figure without escaping to the outside in the radial direction. With respect to leftward rotation, the tip portion escapes radially outward, allowing rotation of the first ring gear R1. The first pawl CW1 on the right side prevents the first ring gear R1 from rotating in the left direction, and allows the first ring gear R1 to rotate in the right direction. As a result, in the bidirectional restriction state shown in FIG. 4A, rotation of the first ring gear R1 in both left and right directions is restricted. Therefore, the first brake B1 is engaged when the first ring gear R1 rotates in both directions.
　第１切替部ＳＷ１は第１切替プレートＰＬ１を有し、第１の爪ＣＷ１の位置を切り替える。図４Ａから図４Ｃでは第１切替部ＳＷ１の第１切替プレートＰＬ１を二点破線で示す。第１切替プレートＰＬ１はリング状の形状を有し、周方向に可動とされる。 The first switching part SW1 has a first switching plate PL1, and switches the position of the first claw CW1. In FIGS. 4A to 4C, the first switching plate PL1 of the first switching unit SW1 is indicated by a two-dot broken line. The first switching plate PL1 has a ring shape and is movable in the circumferential direction.
　第１切替プレートＰＬ１は図４Ａに示す双方向規制状態に対応する位置と、図４Ｂに示す一方向規制状態に対応する位置と、図４Ｃに示す解放状態に対応する位置とを有する。第１切替プレートＰＬ１はウォームホイール３２に設けられ、ウォームホイール３２とともに回転する。従って、第１切替プレートＰＬ１はアクチュエータ３１により周方向に駆動され、これにより第１切替プレートＰＬ１の位置が切り替えられる。 The first switching plate PL1 has a position corresponding to the bidirectional restriction state shown in FIG. 4A, a position corresponding to the one-way restriction state shown in FIG. 4B, and a position corresponding to the release state shown in FIG. 4C. The first switching plate PL1 is provided on the worm wheel 32 and rotates together with the worm wheel 32. Therefore, the first switching plate PL1 is driven in the circumferential direction by the actuator 31, thereby switching the position of the first switching plate PL1.
　例えば、図４Ａに示す状態より右側の定位置に第１切替プレートＰＬ１を回転駆動した場合、第１切替プレートＰＬ１の位置は図４Ｂに示す一方向規制状態に対応する位置に切り替えられる。この際、第１切替部ＳＷ１はばねの付勢力に抗して左側の第１の爪ＣＷ１の先端部を径方向外側に押し出すことで、左側の第１の爪ＣＷ１の位置をフリー位置に切り替える。結果、左側の第１の爪ＣＷ１が第１回転側部材ＲＢ１の係合部から外れるので、右方向への第１リングギアＲ１の回転がフリーとなる。その一方で、この場合は右側の第１の爪ＣＷ１は係合部と係合したままの状態になるので、左方向への第１リングギアＲ１の回転はロックされる。従ってこの場合、第１ブレーキＢ１は右方向への第１リングギアＲ１の回転に対して解放状態になり、左方向への第１リングギアＲ１の回転に対して締結状態になる。 For example, when the first switching plate PL1 is rotationally driven to a fixed position on the right side from the state shown in FIG. 4A, the position of the first switching plate PL1 is switched to a position corresponding to the one-way restriction state shown in FIG. 4B. At this time, the first switching part SW1 switches the position of the left first pawl CW1 to the free position by pushing the tip of the left first pawl CW1 radially outward against the biasing force of the spring. . As a result, the left first pawl CW1 is disengaged from the engagement portion of the first rotating member RB1, and the first ring gear R1 is free to rotate rightward. On the other hand, in this case, the right first pawl CW1 remains engaged with the engaging portion, so the rotation of the first ring gear R1 in the leftward direction is locked. Therefore, in this case, the first brake B1 is released against the rotation of the first ring gear R1 in the rightward direction, and is in the engaged state against the rotation of the first ring gear R1 in the leftward direction.
　図４Ａに示す状態より左側の定位置に第１切替プレートＰＬ１を回転駆動した場合は、第１切替プレートＰＬ１の位置は図４Ｃに示す解放状態に対応する位置に切り替えられる。この際、第１切替部ＳＷ１はばねの付勢力に抗して左右両方の第１の爪ＣＷ１の先端部を径方向外側に押し出すことで、左右両方の第１の爪ＣＷ１の位置をフリー位置に切り替える。結果、左右双方向への第１リングギアＲ１の回転がフリーとなる。 When the first switching plate PL1 is rotationally driven to a fixed position on the left side from the state shown in FIG. 4A, the position of the first switching plate PL1 is switched to a position corresponding to the released state shown in FIG. 4C. At this time, the first switching part SW1 pushes the tips of both the left and right first claws CW1 radially outward against the biasing force of the spring, thereby changing the positions of both the left and right first claws CW1 to the free position. Switch to As a result, the first ring gear R1 can freely rotate in both left and right directions.
　このように、アクチュエータ３１は第１切替プレートＰＬ１を駆動することで第１ブレーキＢ１を駆動する。アクチュエータ３１は第１ブレーキＢ１と同様にして第２ブレーキＢ２も駆動することができる。 In this way, the actuator 31 drives the first brake B1 by driving the first switching plate PL1. The actuator 31 can also drive the second brake B2 in the same manner as the first brake B1.
　次に本実施形態の主な作用効果について説明する。 Next, the main effects of this embodiment will be explained.
　（１）ユニット１００は第１遊星歯車機構ＰＧＭ１と、第２遊星歯車機構ＰＧＭ２と、第１遊星歯車機構ＰＧＭ１に接続された第１ブレーキＢ１と、第２遊星歯車機構ＰＧＭ２に接続された第２ブレーキＢ２と、第１ブレーキＢ１及び第２ブレーキＢ２を駆動するアクチュエータ３１とを有する。径方向視において、第１ブレーキＢ１は第１遊星歯車機構ＰＧＭ１とオーバーラップする部分を有する。径方向視において、第２ブレーキＢ２は第２遊星歯車機構ＰＧＭ２とオーバーラップする部分を有する。軸方向視において、第１遊星歯車機構ＰＧＭ１は第２遊星歯車機構ＰＧＭ２とオーバーラップする部分を有する。アクチュエータ３１は第１ブレーキＢ１及び第２ブレーキＢ２の間に挟まれた部分を有する。 (1) The unit 100 includes a first planetary gear mechanism PGM1, a second planetary gear mechanism PGM2, a first brake B1 connected to the first planetary gear mechanism PGM1, and a second brake B1 connected to the second planetary gear mechanism PGM2. It has a brake B2 and an actuator 31 that drives the first brake B1 and the second brake B2. In a radial view, the first brake B1 has a portion that overlaps with the first planetary gear mechanism PGM1. In a radial view, the second brake B2 has a portion that overlaps with the second planetary gear mechanism PGM2. When viewed in the axial direction, the first planetary gear mechanism PGM1 has a portion that overlaps with the second planetary gear mechanism PGM2. The actuator 31 has a portion sandwiched between a first brake B1 and a second brake B2.
　このような構成によれば、第１ブレーキＢ１及び第２ブレーキＢ２それぞれを第１遊星歯車機構ＰＧＭ１及び第２遊星歯車機構ＰＧＭ２のうち対応する遊星歯車機構それぞれと径方向においてオーバーラップさせることで軸方向の寸法を縮小できる。このため、ユニット１００のレイアウト性が向上する。またこのときには第１ブレーキＢ１及び第２ブレーキＢ２の間に両者が干渉しないようにそれなりのクリアランスが必要になるので、そのスペースを有効利用することにより、ユニット１００のレイアウト性をさらに向上させることができる。 According to such a configuration, by making each of the first brake B1 and the second brake B2 overlap in the radial direction with the corresponding one of the first planetary gear mechanism PGM1 and the second planetary gear mechanism PGM2, the shaft Directional dimensions can be reduced. Therefore, the layout of the unit 100 is improved. Also, at this time, a certain amount of clearance is required between the first brake B1 and the second brake B2 so that they do not interfere with each other, so by making effective use of that space, the layout of the unit 100 can be further improved. can.
　アクチュエータ３１は第１ブレーキＢ１又は第２ブレーキＢ２を駆動するように構成されてもよい。この場合でも同様の作用効果を得ることができる。 The actuator 31 may be configured to drive the first brake B1 or the second brake B2. Even in this case, similar effects can be obtained.
　（２）ユニット１００ではアクチュエータ３１は第１ブレーキＢ１及び第２ブレーキＢ２の双方を駆動する。このような構成によれば、第１ブレーキＢ１と第２ブレーキＢ２とでアクチュエータ３１を共用することにより部品点数を削減でき、部品点数の削減によりユニット１００のレイアウト性向上を図ることもできる。 (2) In the unit 100, the actuator 31 drives both the first brake B1 and the second brake B2. According to such a configuration, the number of parts can be reduced by sharing the actuator 31 between the first brake B1 and the second brake B2, and the layout of the unit 100 can also be improved by reducing the number of parts.
　（３）ユニット１００ではアクチュエータ３１はウォームギア３１１を有する。ウォームギア３１１は第１ブレーキＢ１及び第２ブレーキＢ２の間に挟まれた部分を有し、ウォームギア３１１の長手方向はユニット１００の軸方向と交差する。このような構成によれば、アクチュエータ３１のうちウォームギア３１１を第１ブレーキＢ１及び第２ブレーキＢ２間に挟むにあたり、その長手方向を軸方向と交差させることで、ユニット１００の軸方向の短縮に寄与することができる。 (3) In the unit 100, the actuator 31 has a worm gear 311. The worm gear 311 has a portion sandwiched between the first brake B1 and the second brake B2, and the longitudinal direction of the worm gear 311 intersects with the axial direction of the unit 100. According to such a configuration, when the worm gear 311 of the actuator 31 is sandwiched between the first brake B1 and the second brake B2, its longitudinal direction intersects with the axial direction, thereby contributing to shortening the unit 100 in the axial direction. can do.
　以上、本発明の実施形態について説明したが、上記実施形態は本発明の適用例の一部を示したに過ぎず、本発明の技術的範囲を上記実施形態の具体的構成に限定する趣旨ではない。 Although the embodiments of the present invention have been described above, the above embodiments merely show a part of the application examples of the present invention, and are not intended to limit the technical scope of the present invention to the specific configurations of the above embodiments. do not have.
　１０　　ハウジング
　２０　　変速機構
　２２　　回転軸
　３０　　駆動装置
　３１　　　アクチュエータ
　３１１　　ウォームギア
　１００　　ユニット
　Ｂ１　　　第１ブレーキ（第１係合要素）
　Ｂ２　　　第２ブレーキ（第２係合要素）
　ＣＬ　　　クラッチ
　ＰＧＭ１　第１遊星歯車機構
　ＰＧＭ２　第２遊星歯車機構 10 Housing 20 Transmission mechanism 22 Rotating shaft 30 Drive device 31 Actuator 311 Worm gear 100 Unit B1 First brake (first engagement element)
B2 Second brake (second engagement element)
CL Clutch PGM1 1st planetary gear mechanism PGM2 2nd planetary gear mechanism

Claims (3)

  1. 　第１遊星歯車機構と、
    　第２遊星歯車機構と、
    　前記第１遊星歯車機構に接続された第１係合要素と、
    　前記第２遊星歯車機構に接続された第２係合要素と、
    　前記第１係合要素及び前記第２係合要素の少なくとも一方を駆動するアクチュエータと、
    を有し、
    　径方向視において、前記第１係合要素は前記第１遊星歯車機構とオーバーラップする部分を有し、
    　径方向視において、前記第２係合要素は前記第２遊星歯車機構とオーバーラップする部分を有し、
    　軸方向視において、前記第１遊星歯車機構は前記第２遊星歯車機構とオーバーラップする部分を有し、
    　前記アクチュエータは前記第１係合要素及び前記第２係合要素の間に挟まれた部分を有する、
    ユニット。     a first planetary gear mechanism;
    a second planetary gear mechanism;
    a first engagement element connected to the first planetary gear mechanism;
    a second engagement element connected to the second planetary gear mechanism;
    an actuator that drives at least one of the first engagement element and the second engagement element;
    has
    In a radial view, the first engagement element has a portion that overlaps with the first planetary gear mechanism,
    In a radial view, the second engagement element has a portion that overlaps with the second planetary gear mechanism,
    When viewed in the axial direction, the first planetary gear mechanism has a portion that overlaps with the second planetary gear mechanism,
    The actuator has a portion sandwiched between the first engagement element and the second engagement element.
    unit.
  2. 　請求項１に記載のユニットであって、
    　前記アクチュエータは前記第１係合要素及び前記第２係合要素の双方を駆動する、
    ユニット。     The unit according to claim 1, comprising:
    the actuator drives both the first engagement element and the second engagement element;
    unit.
  3. 　請求項１又は２に記載のユニットであって、
    　前記アクチュエータはウォームギアを有し、
    　前記ウォームギアは前記第１係合要素及び前記第２係合要素の間に挟まれた部分を有し、
    　前記ウォームギアの長手方向は軸方向と交差する、
    ユニット。     The unit according to claim 1 or 2,
    the actuator has a worm gear;
    The worm gear has a portion sandwiched between the first engagement element and the second engagement element,
    The longitudinal direction of the worm gear intersects with the axial direction.
    unit.
PCT/JP2023/024214 2022-08-02 2023-06-29 Unit WO2024029247A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2022123111 2022-08-02
JP2022-123111 2022-08-02

Publications (1)

Publication Number Publication Date
WO2024029247A1 true WO2024029247A1 (en) 2024-02-08

Family

ID=89848831

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2023/024214 WO2024029247A1 (en) 2022-08-02 2023-06-29 Unit

Country Status (1)

Country Link
WO (1) WO2024029247A1 (en)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009262915A (en) * 2008-04-01 2009-11-12 Denso Corp Vehicle driving actuator and vehicle
JP2017521293A (en) * 2014-05-06 2017-08-03 ボルグワーナー スウェーデン エービー Torque vectoring device
JP2018003930A (en) * 2016-06-30 2018-01-11 本田技研工業株式会社 Driving device
WO2020105635A1 (en) * 2018-11-19 2020-05-28 アイシン・エィ・ダブリュ株式会社 Vehicular driving apparatus

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009262915A (en) * 2008-04-01 2009-11-12 Denso Corp Vehicle driving actuator and vehicle
JP2017521293A (en) * 2014-05-06 2017-08-03 ボルグワーナー スウェーデン エービー Torque vectoring device
JP2018003930A (en) * 2016-06-30 2018-01-11 本田技研工業株式会社 Driving device
WO2020105635A1 (en) * 2018-11-19 2020-05-28 アイシン・エィ・ダブリュ株式会社 Vehicular driving apparatus

Similar Documents

Publication Publication Date Title
JP4708467B2 (en) Vehicle drive device
JP6911782B2 (en) Power transmission device
JP2018123722A5 (en)
US9739321B2 (en) Selectable one-way clutch
JP2011106167A5 (en)
WO2020105635A1 (en) Vehicular driving apparatus
CN108953499B (en) Gear transmission device
JP6546300B1 (en) Transmission for motor
WO2024029247A1 (en) Unit
WO2019135331A1 (en) Transmission mechanism
CN113412379A (en) Two-stage speed variator for electric drive vehicle
JP5062122B2 (en) Vehicle drive device
WO2024014130A1 (en) Unit
JP2021014198A (en) In-wheel motor type drive unit
WO2024014129A1 (en) Unit
WO2024029248A1 (en) Transmission control device, transmission control method, and program
WO2024014120A1 (en) Unit
WO2023171054A1 (en) Device
JP7476873B2 (en) Power transmission
WO2024062708A1 (en) Unit
WO2024014119A1 (en) Unit
WO2024014124A1 (en) Unit
WO2024014122A1 (en) Unit
WO2024014121A1 (en) Unit
WO2024014127A1 (en) Unit

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 23849806

Country of ref document: EP

Kind code of ref document: A1

DPE1 Request for preliminary examination filed after expiration of 19th month from priority date (pct application filed from 20040101)